粉料壓片機的減速器設(shè)計【干粉壓片機】【說明書+CAD】
粉料壓片機的減速器設(shè)計【干粉壓片機】【說明書+CAD】,干粉壓片機,說明書+CAD,粉料壓片機的減速器設(shè)計【干粉壓片機】【說明書+CAD】,壓片,減速器,設(shè)計,干粉,說明書,仿單,cad
機械基礎(chǔ)綜合設(shè)計說明書BIT機械基礎(chǔ)綜合課程設(shè)計說明書設(shè)計題目:粉料壓片機班級: 姓名: 學號:設(shè)計題目:粉料壓片機、已知數(shù)據(jù):1原動機選擇三相交流異步電動機,同步轉(zhuǎn)速 為1500 r/min或1000r/min。2該機械系統(tǒng)要求設(shè)計為單自由度的機械。3壓片時的最大阻力為F=6000N4生產(chǎn)率為每分鐘壓制40片,即沖頭每分鐘往 復運動40次5模具厚度為h=50mm,料斗高度為30mm。 (設(shè)計上沖頭最高極限位置參考)6沖壓工藝流程圖。7傳動裝置的使用壽命預定為10年,單班制, 每班工作8小時。8減速器方案為:V帶加錐、圓柱齒輪減速器、設(shè)計計算 機構(gòu)系統(tǒng)運動方案: 上沖頭加壓機構(gòu)尺度綜合各桿長度設(shè)計: 上沖頭加壓機構(gòu)運動分析 上沖頭加壓機構(gòu)受力分析其中一個位置上的受力分析: (五)電機的選擇電動機類型和結(jié)構(gòu)形式的選擇按工作要求和工作條件,選用Y系列三相交流異步電動機。電動機功率的確定工作機所需功率Pw由 Pw=2Fv1000kW式中,2表示工作機有兩個沖頭;F為工作阻力,有F=6000N;v為工作機的平均速度,令上沖頭的沖程為s=60mm(50/2+30)mm有v=N2s10-360=8.00010-2m/s則有Pw=2Fv1000=260008.00010-21000=0.960kW所需電動機功率Pd由Pd=Pw式中,Pw已知;為由電動機至工作機的總效率,有=12432435其中 1-V帶傳動效率取0.96 2-滾子軸承傳動效率取0.983-齒輪傳動效率取0.974-聯(lián)軸器傳動效率取0.995-連桿機構(gòu)傳動效率取0.6故 0.4850 Pd=Pw=1.979kW電動機額定功率Ped對于載荷比較穩(wěn)定、長期運轉(zhuǎn)的機械,只需使所選電動機的額定功率Ped等于或稍大于所需電動機功率Pd,即PedPd就可以。因此選擇額定功率為2.2kW的電動機。電動機轉(zhuǎn)速的確定電動機的轉(zhuǎn)速高,磁極對數(shù)少,尺寸和質(zhì)量小,價格也低,但傳動裝置的傳動比大,從而使傳動裝置的結(jié)構(gòu)尺寸增大,成本提高;選用低轉(zhuǎn)速的電動機則相反。一般來說,無特殊,通常多選用同步轉(zhuǎn)速為1500r/min或1000r/min的電動機。綜上所述,初選電機如下表方案電動機型號額定功率(kW)電動機轉(zhuǎn)速(r/min)電動機質(zhì)量(kg)同步滿載1Y100L1-42.215001420342Y112M-62.2100094045 本設(shè)計選擇同步轉(zhuǎn)速為1000r/min的電動機。具體參數(shù)如下:型號額定功率(kw)同步轉(zhuǎn)速(r/min)滿載轉(zhuǎn)速(r/min)堵轉(zhuǎn)轉(zhuǎn)矩額定轉(zhuǎn)矩最大轉(zhuǎn)矩額定轉(zhuǎn)矩電機質(zhì)量(kg)Y112M-62.210009402.02.034(六)、傳動系統(tǒng)的運動參數(shù)、動力參數(shù)的計算總傳動比的確定及各級傳動比的分配傳動裝置總傳動比根據(jù)電機滿載轉(zhuǎn)速nm和工作機轉(zhuǎn)速nw,可得傳動裝置的總傳動比為i=nmnw=94040=23.5各級傳動比分配取V帶傳動比為i1=2.5,則減速器的傳動比為i減=ii1=23.52.5=9.4查機械設(shè)計課程設(shè)計指導書根據(jù)圓錐-圓柱齒輪減速器傳動比的分配,取錐齒輪的傳動比i2=0.25i減則取i2=2.35 i3=4運動條件及運動參數(shù)分析計算各軸的標記如下:0代表電動機的輸出軸,1代表小帶輪軸,2代表大帶輪,3代表減速器高速軸,4代表減速器中間軸,5代表減速器低速軸 0軸:1軸: 2軸: 3軸: 4軸: 5軸:各軸運動和動力參數(shù)匯總表軸名功率P/KW轉(zhuǎn)矩T/(Nmm)轉(zhuǎn)速n/(r/min)0軸1.97920105.89401軸1.95920104.79402軸1.806 45870.53763軸1.71743610.03764軸1.63297410.01605軸1.551 370391.840(七)V帶傳動裝置設(shè)計校核已知條件:電機為Y112M-6型電動機,額定功率P=2.2KW,同步轉(zhuǎn)速=1000r/min,傳動比i=2.5,單班制工作解:1. 確定計算功率根據(jù)給定的工作條件,查表得工作情況系數(shù)=1.2,=2.64kW2. V帶截面型號選擇由額定功率和轉(zhuǎn)速查圖并驗證后,選A型V帶3. 確定帶輪基準直徑,根據(jù)型號查表選擇:=90mm根據(jù)傳動比確定從動輪直徑:=225mm據(jù)表選取最接近的標準直徑為=224mm4. 驗算帶速vV帶傳動帶速為 =4.427m/s25m/s,帶速適宜5. 確定中心距a和帶的基準長度初定中心距 ,得219.8628(mm), 初定中心距=500mm帶的基準長度初值 =1502mm查表確定基準長度=1600mm實際中心距 =547.5mm安裝時應保證的中心距a在下面的范圍內(nèi):523.5=595.5(mm)6. 校核小帶輪包角=166,大于120,合格7. 確定傳動V帶根數(shù)Z查表得: 長度系數(shù)=0.99,包角系數(shù)=0.96單根帶基本額定功率=0.77kW,單根帶額定功率增量=0.02kW=3.516,取V帶根數(shù)Z=48. 確定初拉力和軸上壓力查表得,帶單位長度質(zhì)量 q=0.1kg/m初拉力 =120.9N軸上壓力 =962.7N(八) 減速器設(shè)計直齒圓錐齒輪傳動設(shè)計(主要參照教材機械設(shè)計(第八版)已知輸入功率為=1.717kw、小齒輪轉(zhuǎn)速為=376r/min、齒數(shù)比為2.35由電動機驅(qū)動。工作壽命10年,單班制,工作平穩(wěn),轉(zhuǎn)向不變。 1、選定齒輪類型、精度等級、材料及齒數(shù) (1)圓錐圓錐齒輪減速器為通用減速器,其速度不高,故選用7級精度(GB10095-88) (2)材料選擇 由機械設(shè)計(第八版)表10-1 小齒輪材料可選為40Cr(調(diào)質(zhì)),硬度為280HBS,大齒輪材料取45鋼(調(diào)質(zhì)),硬度為240HBS,二者材料硬度相差40HBS。(3) 選小齒輪齒數(shù),則大齒輪齒數(shù) 2、按齒面接觸疲勞強度設(shè)計 設(shè)計計算公式: (1) 、確定公式內(nèi)的各計算值1) 試選載荷系數(shù)=1.82) 小齒輪傳遞的轉(zhuǎn)矩=95.510=43.61KN.Mm3) 取齒寬系數(shù)4) 查圖10-21齒面硬度得小齒輪的接觸疲勞強度極限650Mpa 大齒輪的接觸疲勞極限550Mpa 5) 查表10-6選取彈性影響系數(shù)=189.8 6) 由教材公式10-13計算應力值環(huán)數(shù) N=60nj =603761(836510)=6.5910h N=2.810h7) 查教材10-19圖得:K=0.91 K=0.958) 齒輪的接觸疲勞強度極限:取失效概率為1%,安全系數(shù)S=1,應用公式(10-12)得: =0.91650=591.5 =0.95550=522.5 設(shè)計計算1) 試算小齒輪的分度圓直徑,帶入中的較小值得 2) 計算圓周速度V 1.52m/s3) 計算載荷系數(shù) 系數(shù)=1,根據(jù)V=1.52m/s,7級精度查圖表(圖10-8)得動載系數(shù)=1.05 查圖表(表10-3)得齒間載荷分布系數(shù)=1.1 根據(jù)大齒輪兩端支撐,小齒輪懸臂布置查表10-9得=1.25的=1.5X1.25=1.875 得載荷系數(shù) =2.164) 按實際的載荷系數(shù)校正所得的分度圓直徑,得 = 5)計算模數(shù)M 3、按齒根彎曲疲勞強度設(shè)計 設(shè)計公式: m(1) 確定公式內(nèi)各計算數(shù)值1) 計算載荷系數(shù) =1X1.15X1X1.875=2.162) 計算當量齒數(shù) =27.17 =150.63) 由教材表10-5查得齒形系數(shù) 應力校正系數(shù) 4) 由教材圖20-20c查得小齒輪的彎曲疲勞強度極限,大齒輪的彎曲疲勞強度極限5) 由機械設(shè)計圖10-18取彎曲疲勞壽命系數(shù)K=0.87 K=0.896) 計算彎曲疲勞許用應力取彎曲疲勞安全系數(shù),得 = =7) 計算大小齒輪的,并加以比較 大齒輪的數(shù)值大,選用大齒輪的尺寸設(shè)計計算.(2) 設(shè)計計算 取M=2.5mm 對比計算結(jié)果,由齒面接觸疲勞強度計算的模數(shù)m大于由齒根彎曲疲勞強度計算的模數(shù),由于齒輪模數(shù)的大小主要取決于彎曲強度所承載的能力。而齒面接觸疲勞強度所決定的承載能力,取決于齒輪直徑。按GB/T1357-1987圓整為標準模數(shù),取m=2. 5mm但為了同時滿足接觸疲勞強度,需要按接觸疲勞強度算得的分度圓直徑d=81.7來計算應有的齒數(shù).計算齒數(shù) z=32.68 取z=33 那么z=2.3533=77.55取z=78 4、計算幾何尺寸(1) d=82.5 (2) d=195(3) =22.(4)(5) =105.9mm mm(6) =37.07圓整取=40mm =45mm斜齒圓柱齒輪傳動的設(shè)計(主要參照教材機械設(shè)計(第八版)已知輸入功率為=1.632kw、小齒輪轉(zhuǎn)速為=160r/min、齒數(shù)比為4。工作壽命10年,單班制,工作平穩(wěn),轉(zhuǎn)向不變。 1、選定齒輪類型、精度等級、材料及齒數(shù) (1)運輸機為一般工作機器,速度不高,故選用7級精度。(GB10095-88) (2)材料選擇 由機械設(shè)計(第八版)表10-1小齒輪材料為40Cr(調(diào)質(zhì)),硬度為280HBS,大齒輪材料為45鋼(調(diào)質(zhì)),硬度為240HBS,二者材料硬度相差40HBS。(3) 選小齒輪齒數(shù),則大齒輪齒數(shù) 初選螺旋角。 2、按齒面接觸疲勞強度計算按下式設(shè)計計算 (1)確定公式內(nèi)的各計算數(shù)值1) 試選載荷系數(shù)=1.62) 查教材圖表(圖10-30)選取區(qū)域系數(shù)=2.4353) 查教材表10-6選取彈性影響系數(shù)=189.8 4) 查教材圖表(圖10-26)得 =0.765 =0.88 =1.6455) 由教材公式10-13計算應力值環(huán)數(shù)N=60nj =601601(836510)=2.810h N=0.7X10h6) 查教材10-19圖得:K=0.95 K=0.997) 查取齒輪的接觸疲勞強度極限650Mpa 550Mpa 8) 由教材表10-7查得齒寬系數(shù)=19) 小齒輪傳遞的轉(zhuǎn)矩=97.41N.m10) 齒輪的接觸疲勞強度極限:取失效概率為1%,安全系數(shù)S=1,應用公式(10-12)得:=0.95650=617.5 =0.99550=544.5 許用接觸應力為 (2) 設(shè)計計算1) 按式計算小齒輪分度圓直徑 =2) 計算圓周速度0.445m/s3) 計算齒寬b及模數(shù) b=53.12mm =4) 計算齒寬與高之比 齒高h= =2.252.34=5.27 = =10.085) 計算縱向重合度 =0.318tan=0.318x1x22tan=1.7446) 計算載荷系數(shù)K 系數(shù)=1,根據(jù)V=0.445m/s,7級精度查圖表(圖10-8)得動載系數(shù)=1.01 查教材圖表(表10-3)得齒間載荷分布系數(shù)=1.2 由教材圖表(表10-4)查得=1.420 查教材圖表(圖10-13)得=1.32 所以載荷系數(shù) =1.727) 按實際載荷系數(shù)校正所算得的分度圓直徑 =8) 計算模數(shù) = 3、按齒根彎曲疲勞強度設(shè)計 由彎曲強度的設(shè)計公式設(shè)計(1) 確定公式內(nèi)各計算數(shù)值1) 計算載荷系數(shù) =1.602) 根據(jù)縱向重合度=1.744 查教材圖表(圖10-28)查得螺旋影響系數(shù)=0.883) 計算當量齒數(shù) =24.09 =96.374) 查取齒形系數(shù) 查教材圖表(表10-5)=2.6476 ,=2.187345) 查取應力校正系數(shù) 查教材圖表(表10-5)=1.5808 ,=1.786336) 查教材圖表(圖10-20c)查得小齒輪彎曲疲勞強度極限=520MPa ,大齒輪彎曲疲勞強度極限=400MPa 。7) 查教材圖表(圖10-18)取彎曲疲勞壽命系數(shù)K=0.89 K=0.92 8) 計算彎曲疲勞許用應力。 取彎曲疲勞安全系數(shù)S=1.4,由式得 = =9) 計算大、小齒輪的,并加以比較 大齒輪的數(shù)值大.選用大齒輪的參數(shù)計算.(2) 設(shè)計計算1) 計算模數(shù) 對比計算結(jié)果,由齒面接觸疲勞強度計算的法面模數(shù)m大于由齒根彎曲疲勞強度計算的法面模數(shù),由于齒輪模數(shù)的大小主要取決于彎曲強度所承載的能力。而齒面接觸疲勞強度所決定的承載能力,僅取決于齒輪直徑。按GB/T1357-1987圓整為標準模數(shù),取m=2mm但為了同時滿足接觸疲勞強度,需要按接觸疲勞強度算得的分度圓直徑d=54.39來計算應有的齒數(shù).2)計算齒數(shù) z=26.4 取z=27 那么z=427=1084、 幾何尺寸計算(1)計算中心距 a=139 取a=140mm(2)按圓整后的中心距修正螺旋角 =arccos 因值改變不多,故參數(shù),等不必修正.(3)計算大.小齒輪的分度圓直徑 d=56.25 d=225(4)計算齒輪寬度 B= 圓整取 高速軸、中間軸、輸出軸設(shè)計計算軸的設(shè)計計算已知條件:軸的傳遞功率P=1.717kW,轉(zhuǎn)速n376r/min,小錐齒輪的分度圓直徑為:d82.5mm,寬度為:b=45 mm 1. 選擇軸材料及熱處理方式;由于減速器為一般用途軸,故選45鋼,調(diào)質(zhì),查表得,;2. 最小軸徑估算 對軸均使用扭轉(zhuǎn)強度法,根據(jù)公式 mm可知,對于軸,P=1.717kW, C=120,n376r/min .故最小軸徑為dmin=17.9mm;經(jīng)圓整,取最小軸徑d=18mm;3 軸的結(jié)構(gòu)設(shè)計高速軸軸系的結(jié)構(gòu)如圖所示。(1)各軸段直徑的確定從左到右:1) 最小直徑,安裝大帶輪軸段,確定軸徑18mm。2) 端蓋處軸的直徑為20mm2)軸承處軸段,根據(jù)角接觸軸承7205C確定軸徑25mm3)軸環(huán)段取32mm4)軸承處根據(jù)角接觸軸承7205C取25mm5)小錐齒輪處取20mm(2)軸各段長度從左到右:1) 由選擇的大帶輪取70mm2) 由箱體結(jié)構(gòu)、軸承端蓋、裝配關(guān)系等確定26mm3) 由角接觸軸承確定15mm4) 由裝配關(guān)系、箱體結(jié)構(gòu)確定46mm5) 由角接觸軸承確定15mm6) 由套筒及小錐齒輪確定42mm4 按彎扭合成法校核軸的強度(1) 計算小錐齒輪的受力 水平面內(nèi)受力Me=71.36N.m(2) 計算水平面內(nèi)彎矩,繪制水平彎矩(MH)圖 (3) 垂直面內(nèi)受力 繪制垂直面彎矩(M)圖 Me=77.89 N.mME=100.97 N.m N.m 8合成彎矩(M)圖 T=49.24 N.m轉(zhuǎn)矩(T)圖 (4) 確定危險截面,校核軸的強度E截面處受轉(zhuǎn)矩和彎矩最大W=0.1d3 為軸的抗彎截面系數(shù),取0.6 ,代入數(shù)據(jù)則有=20.56MPa=60MPa結(jié)論:軸的結(jié)構(gòu)滿足強度要求5. 按安全系數(shù)法精確校核軸的強度 (1)查表可得,對于A型平鍵,軸上鍵槽的應力集中系數(shù)為:(2)查表可得,45鋼的絕對尺寸系數(shù)為: (3)對于45鋼,彎矩和轉(zhuǎn)矩作用下軸的平均應力折算為應力幅的等效系數(shù)分別為: (4)查表可得,該軸段的加工表面質(zhì)量系數(shù): ,(5)由于該軸所受彎曲應力為對稱循環(huán)變應力,故平均應力 彎曲應力幅 =9.75Mpa(6)由于該軸所受扭轉(zhuǎn)切應力為脈動循環(huán)變應力,故 扭轉(zhuǎn)切應力 =30.48MPa轉(zhuǎn)矩應力幅和平均應力 =15.24MPa(7)根據(jù)上式可得,僅考慮彎曲應力和僅考慮扭轉(zhuǎn)切應力時的工作安全系數(shù)分別為:=5.6, =7.2(8)可得軸的工作安全系數(shù)為: =4.42查表,取軸疲勞強度的許用安全系數(shù)為 結(jié)論:,滿足強度要求。 D截面的強度精確校核方法與C截面相同。計算后得到D截面的工作安全系數(shù):=5.61 結(jié)論:,滿足強度要求。軸的設(shè)計計算已知條件:軸的傳遞功率P=1.632kW,轉(zhuǎn)速n160r/min,兩齒輪的分度圓直徑分別為:d1195mm,d256.25mm。 1. 選擇軸材料及熱處理方式;由于減速器為一般用途軸,故選45鋼,調(diào)質(zhì),查表得,;2. 最小軸徑估算 對軸均使用扭轉(zhuǎn)強度法,根據(jù)公式 mm可知,對于軸,P=1.632kW,n160r/min, C=120.故最小軸徑為dmin1=24.68mm;經(jīng)圓整,取最小軸徑d=25mm;3軸的結(jié)構(gòu)設(shè)計軸的結(jié)構(gòu)設(shè)計如圖所示(1)各軸段直徑的確定從左到右:1)最小直徑,安裝角接觸軸承7205C,確定軸徑25mm,長35mm。2)安裝小斜齒輪確定軸徑30mm,長58mm3)軸環(huán)段軸徑取40mm,長13mm4)安裝大錐齒輪軸徑取30mm,長38mm5)安裝角接觸軸承7205C,確定軸徑25mm,長42mm。4按彎扭合成法校核軸的強度(1)建立力學模型 計算齒輪2、3的受力根據(jù)大錐齒輪與小錐齒輪的作用力與反作用力的關(guān)系則有:大錐齒輪: Ft=1281.5N, Fr=181.9N, Fa=429.1N小圓柱斜齒輪 : 水平面內(nèi)受力(2)計算水平面內(nèi)彎矩,繪制水平彎矩(MH)圖 Me=158.1 N.mMc=106.6 N.m(3)垂直面內(nèi)受力 繪制垂直面彎矩(M)圖 MC=67.3N.m ME=40.7 N.mMC=132.4 N.mME=171.8 N.m合成彎矩(M)圖 轉(zhuǎn)矩(T)圖 T=101 N.m(4) 確定危險截面,校核軸的強度E截面處受轉(zhuǎn)矩和彎矩最大C截面處雖然彎矩、轉(zhuǎn)矩不是最大,但軸徑較小該軸的危險截面為C、E兩截面。 C截面 =38.54MPaE截面 =49.35MPa結(jié)論:軸的結(jié)構(gòu)滿足強度要求。 5. 按安全系數(shù)法精確校核軸的強度 (1)查表可得,對于A型平鍵,軸上鍵槽的應力集中系數(shù)為:(2)查表可得,45鋼的絕對尺寸系數(shù)為: (3)對于45鋼,彎矩和轉(zhuǎn)矩作用下軸的平均應力折算為應力幅的等效系數(shù)分別為: (4)查表可得,該軸段的加工表面質(zhì)量系數(shù): ,(5)由于該軸所受彎曲應力為對稱循環(huán)變應力,故平均應力 彎曲應力幅 =19.36Mpa(6)由于該軸所受扭轉(zhuǎn)切應力為脈動循環(huán)變應力,故 扭轉(zhuǎn)切應力 =14.24MPa轉(zhuǎn)矩應力幅和平均應力 =7.1MPa(7)根據(jù)上式可得,僅考慮彎曲應力和僅考慮扭轉(zhuǎn)切應力時的工作安全系數(shù)分別為:=3.02,=2.85(8)可得軸的工作安全系數(shù)為: =2.10查表,取軸疲勞強度的許用安全系數(shù)為 結(jié)論:,滿足強度要求。 D截面的強度精確校核方法與C截面相同。計算后得到D截面的工作安全系數(shù):=2.68 結(jié)論:,滿足強度要求。軸的設(shè)計計算已知條件:軸的傳遞功率P=1.551kW,轉(zhuǎn)速n40r/min,1. 軸材料及熱處理方式;由于減速器為一般用途軸,故選45鋼,調(diào)質(zhì),查表得,;2. 最小軸徑估算 對軸均使用扭轉(zhuǎn)強度法,根據(jù)公式 mm可知,對于軸,P=1.551kW, C=120,n40r/min .故最小軸徑為dmin1=31.58mm;經(jīng)圓整,取最小軸徑d=32mm;3軸的結(jié)構(gòu)設(shè)計軸的結(jié)構(gòu)如圖所示從左到右:1)根據(jù)角接觸軸承7207C,軸直徑35mm,長度38mm。2)安裝大斜齒輪,軸段直徑41mm,長度53mm。3)軸肩直徑52mm 長度10mm4)此段用來軸承的軸向定位軸徑為41mm,長度為70mm5)根據(jù)角接觸軸承7207C,軸直徑35mm,長度57mm。6)軸端最小直徑,用來連接連桿機構(gòu),軸直徑32mm,長度82mm4按彎扭合成法校核軸的強度 (1)計算大圓柱齒輪的受力根據(jù)大圓柱齒輪與小圓柱齒輪的作用力與反作用力有:Ft=3607.8N, Fr=1367.96N,F(xiàn)a=1313.2N水平面內(nèi)受力(2)計算水平面內(nèi)彎矩,繪制水平彎矩(MH)圖 Me=131.7N.m(3)垂直面內(nèi)受力 ME1=81.9N.m N.m繪制垂直面彎矩(M)圖 ME2=54.3N.m合成彎矩(M)圖 ME2=102.5N.mME1=155.1N.mT=390.9N.m轉(zhuǎn)矩(T)圖 (4) 確定危險截面,校核軸的強度E截面處受轉(zhuǎn)矩和彎矩最大 =16.8MPa結(jié)論:軸的結(jié)構(gòu)滿足強度要求。 5. 按安全系數(shù)法精確校核軸的強度 (1)查表可得,對于A型平鍵,軸上鍵槽的應力集中系數(shù)為:(2)查表可得,45鋼的絕對尺寸系數(shù)為: (3)對于45鋼,彎矩和轉(zhuǎn)矩作用下軸的平均應力折算為應力幅的等效系數(shù)分別為: (4)查表可得,該軸段的加工表面質(zhì)量系數(shù): ,(5)由于該軸所受彎曲應力為對稱循環(huán)變應力,故平均應力 彎曲應力幅 =32.6Mpa(6)由于該軸所受扭轉(zhuǎn)切應力為脈動循環(huán)變應力,故 扭轉(zhuǎn)切應力 =19.8MPa轉(zhuǎn)矩應力幅和平均應力 =9.9MPa(7)根據(jù)上式可得,僅考慮彎曲應力和僅考慮扭轉(zhuǎn)切應力時的工作安全系數(shù)分別為: =4.5, =7.6(8)可得軸的工作安全系數(shù)為: =3.88查表,取軸疲勞強度的許用安全系數(shù)為 結(jié)論:,滿足強度要求。 D截面的強度精確校核方法與C截面相同。計算后得到D截面的工作安全系數(shù):=3.12 結(jié)論:,滿足強度要求。 軸承設(shè)計與壽命計算軸的滾動軸承的設(shè)計計算與校核已知:小錐齒輪平均分度圓直徑dm82.5mm,所受圓周力Ft=1281.5N,徑向力Fr=429.1N,軸向力Fa=181.9N,軸的轉(zhuǎn)速n=376r/min,工作溫度低于100C.解:1. 查取7205C軸承的基本參數(shù)由手冊得:Cr=16500N,e=0.38,X=0.44, Y=1.47;2. 計算派生軸向力1)計算滾動軸承的徑向支反力Fr2, Fr1水平支反力兩軸承之間的距離為61mm,右軸承離錐齒輪的距離為35mm 得:735N 得:2017N垂直支反力 得:166N 得:425N合成支反力753.5N 2061.3N2)計算派生軸向力S1和S2=286.33N =783.29N3求軸承的軸向載荷Fa1和Fa2=468.23N=783.29N軸承1為“壓緊”軸承, 軸承2為“放松”軸承軸承1: =97.23N 軸承2: =783.29N4. 計算軸承的當量動載荷PFa1Fr1=0.12929200h(10年)軸的滾動軸承的設(shè)計計算與校核已知:大錐齒輪平均分度圓直徑dm195mm,所受圓周力Ft1=1281.5N,徑向力Fr1=181.9N,軸向力Fa1=429.1N,軸的轉(zhuǎn)速n=160r/min,工作溫度低于100C。小圓柱齒輪分度圓直徑為d2=56.25mm,所受切向力Ft2=3607.8N,徑向力Fr2=1367.96N,軸向力Fa2=1313.2N。解:1. 查取7008C軸承的基本參數(shù)由手冊得:Cr=16500N,e=0.38,X=0.44 Y=1.47;2. 計算派生軸向力1)計算滾動軸承的徑向支反力Fr2, Fr1水平支反力左軸承至第一個齒輪的距離為50mm,兩齒輪的距離為64mm,第二個齒輪離右軸承的距離為60mm. 得:2157.4N 得:2731.9N垂直支反力 得:187N 得:1373N合成支反力2165.1N 3057.6N2)計算派生軸向力S1和S2=822.7N =1161.9N3求軸承的軸向載荷Fa1和Fa2=1706.7N1161.9N軸承2為“壓緊”軸承, 軸承1為“放松”軸承軸承1: Fa1=S1=822.7 軸承2:Fa2=S1+Fa=1706.74. 計算軸承的當量動載荷PFa1Fr1=0.38=e Fa2Fr2=0.55e 軸承1: P1=Fr1=2165 軸承2: P2=XFr+YFa=3854.35. 計算軸承的壽命 工作溫度低于1000C: ft=1=37020h29200h(10年)軸的滾動軸承的設(shè)計計算與校核已知:大圓柱齒輪分度圓直徑d225mm,所受圓周力Ft=3607.8N,徑向力Fr=1367.9N,軸向力Fa=1313.2N,軸的轉(zhuǎn)速n=40r/min,工作中有中等沖擊,工作溫度低于100C 解:1.查取7207C軸承的基本參數(shù)由手冊得:Cr=30500N,e=0.38,X=0.4,Y=1.47;2.計算派生軸向力1)計算滾動軸承的徑向支反力Fr2, Fr1水平支反力 得:2426.3N 得:1181.5N垂直支反力 得:1869.2N 得:782.6N合成支反力3186N 3697N2)計算派生軸向力S1和S2=1211N =1405N3求軸承的軸向載荷Fa1和Fa2=3052N=1211N軸承1為“壓緊”軸承, 軸承2為“放松”軸承軸承1: =3052N 軸承2: =1405N4. 計算軸承的當量動載荷P=0.38 軸承1: =5888N軸承2: =3697N5. 計算軸承的壽命 工作溫度低于1000C: ft=1=40365h29200h(10年)(6) 鍵連接的設(shè)計計算軸帶輪上的鍵:已知條件:軸傳遞的扭矩T=43.61Nm;軸的直徑d=20mm; 鍵的長度=63mm; 鍵的高度=6mm.;材料:45鋼; =150 MPa。根據(jù)普通平鍵的擠壓強度條件:=23.07MPa軸大齒輪上的鍵:已知條件:軸傳遞的扭矩T=97.41Nm;軸的直徑d=30mm; 鍵的長度=32mm; 鍵的高度=8mm.;材料:45鋼; =150 MPa。根據(jù)普通平鍵的擠壓強度條件:=50.73MPa軸大齒輪上的鍵:已知條件:鍵傳遞的扭矩T=370.39Nm;軸的直徑d=41mm; 鍵的長度=50mm; 鍵的高度=8mm.;材料:45鋼; =150 MPa。根據(jù)普通平鍵的擠壓強度條件:=90.24MPa(六) 減速器箱體設(shè)計減速器箱體尺寸如下表所示:名稱符號尺寸關(guān)系結(jié)果mm機座壁厚0.0125(d1+d2)88機蓋壁厚8機座凸緣厚度b1.512機蓋凸緣厚度b11.512機座底凸緣厚度P2.520地腳螺釘直徑12地腳螺釘數(shù)目n查手冊6軸承旁連接螺栓直徑d10.75 df12機蓋機座連接螺栓直徑d2(0.50.6)df8連接螺栓d2的間距150200160軸承端蓋螺釘直徑d3(0.40.5)df 7窺視孔蓋螺釘直徑d4(0.30.4)df5定位銷直徑d(0.70.8) d27df d1 d2 至外機壁距離c12020df、d2之凸緣的距離c21818軸承旁凸臺半徑R199凸臺高度h4040外機壁至軸承座端面距離L1c1+c2+(510)40內(nèi)機壁至軸承座端面距離L258大齒輪頂圓與內(nèi)機壁距離12齒輪端面與內(nèi)機壁距離25機蓋、機座肋厚m1,m2m10.85,m20.857軸承端蓋外徑D2D+(55.5)d390 10軸承端蓋凸緣厚度e1.2d38軸承旁連接螺栓距離s110(七) 體會通過這二十多天的課程設(shè)計,我深深體會到,要設(shè)計一個機械產(chǎn)品,哪怕機構(gòu)并不復雜,也不是一件輕松的事情,需要綜合運用學過的一切機械設(shè)計方面的知識和理論力學、材料力學、數(shù)學、工程材料等各方面的知識,綜合運用各種先進的繪圖、計算軟件,減少工作量和提高設(shè)計效率。我還深刻的體會到,機械的設(shè)計不是一項一個兩個人能完成的工作,需要團隊合作,集思廣益,充分調(diào)動大家的積極性,互相鼓勵、互相幫助、互相批評。對于一個新的機械產(chǎn)品,首先必須舍得拿出時間從總體上綜合考慮、分析,參考已有的、成熟的機構(gòu),盡可能地考慮到一切可能出現(xiàn)的技術(shù)細節(jié),磨刀不誤砍柴工,只有這樣做了,才能在在接下來的設(shè)計中少走彎路,提高效率。這次課程設(shè)計,我感覺工作量相當大,每天都是在加班加點地干,對我的體力和毅力是個很大的考驗,這一點上我明白了作為一個優(yōu)秀的設(shè)計人員,必須有好的身體和堅韌不拔的精神,看似枯燥無味的工作,堅持到最后就會有巨大的成就感,就會有看到產(chǎn)品成功問世的喜悅感!(八) 參考資料機械制圖機械原理機械設(shè)計機械基礎(chǔ)綜合課程設(shè)計其中:曲柄AB=56.6mm,連桿BC=80mm,擺桿CD=150mm,連桿DE=170mm5mm=2.062535編號無錫太湖學院畢業(yè)設(shè)計(論文)相關(guān)資料題目:單級減速機箱體和箱蓋工藝工裝設(shè)計 機電 系 機械工程及自動化專業(yè)學 號: 0923199學生姓名: 張亞東 指導教師: 鮑虹蘇(職稱:高工 ) (職稱: )2013年5月25日目 錄一、畢業(yè)設(shè)計(論文)開題報告二、畢業(yè)設(shè)計(論文)外文資料翻譯及原文三、學生“畢業(yè)論文(論文)計劃、進度、檢查及落實表”四、實習鑒定表無錫太湖學院畢業(yè)設(shè)計(論文)開題報告題目:單級減速機箱體和箱蓋工藝工裝設(shè)計 信機 系 機械工程及自動化專業(yè)學 號: 0923199 學生姓名: 張亞東 指導教師: 鮑虹蘇 ( 職稱:高工) (職稱: )2012年11月24日 課題來源機械制造業(yè)是一個國家最基礎(chǔ)的行業(yè),也決定了一個國家制造業(yè)的整體水平現(xiàn)在中國已經(jīng)是一個制造大國,中國的制造業(yè)規(guī)模已經(jīng)達到世界第四位,僅次于美國、日本和德國。研究內(nèi)容本設(shè)計是針對減速機箱體工藝的制作,主要研究的是減速機箱蓋的工藝過程、減速機的底座的工藝過程、減速機箱體合裝后的工藝過程以及對該技術(shù)的測試和其實用性的研究。并由此做出了對現(xiàn)行的減速機的箱體的改造和進一步的完善。在這次的箱體工藝制造中,對一些主要程序比如說結(jié)合面聯(lián)接孔、鉆頂面螺紋底孔、攻螺紋、鉆側(cè)面測油孔、放油孔、螺紋底孔、沉孔、攻螺紋 等的研究。擬采取的研究方法、技術(shù)路線、實驗方案及可行性分析設(shè)計任務1) 設(shè)計一個中等復雜的零件的加工工藝規(guī)程;2) 設(shè)計一個專用夾具;3) 編寫設(shè)計說明書。根據(jù)設(shè)計任務做出減速機箱的基本設(shè)計任務1)繪制零件工件圖一張;2)繪制毛坯零件合圖一張;3)編制機械加工工藝規(guī)程卡片一套;4)編寫設(shè)計說明書一份;5)收集和研究原始資料,為夾具結(jié)構(gòu)設(shè)計做好技術(shù)準備。6)初步擬定夾具結(jié)構(gòu)方案,繪制夾具結(jié)構(gòu)草圖,進行必要的理論計算和分析。選擇最佳的夾具結(jié)構(gòu)方案,確定夾具精度和夾具總圖尺寸、公差配合與技術(shù)要求。7) 繪制夾具總圖和主要非標準件零件圖,編寫設(shè)計說明書。8)編制夾具特殊使用維護、操作、制造方面的說明或技術(shù)要求。研究計劃及預期成果研究計劃:2012年11月12日-2012年12月25日:按照任務書要求查閱論文相關(guān)參考資料,填寫畢業(yè)設(shè)計開題報告書。2013年1月11日-2013年3月5日:填寫畢業(yè)實習報告。2013年3月8日-2013年3月14日:按照要求修改畢業(yè)設(shè)計開題報告。2013年3月15日-2013年3月21日:學習并翻譯一篇與畢業(yè)設(shè)計相關(guān)的英文材料。2013年3月22日-2013年4月11日:設(shè)計減速機箱體和箱蓋的結(jié)構(gòu)并畫出相關(guān)草圖2013年4月12日-2013年4月25日:完善設(shè)計所需的各種零件圖、夾具圖,并對設(shè)計的所有數(shù)據(jù)進行整理,做好撰寫畢業(yè)論文的準備。2013年4月26日-2013年5月20日:畢業(yè)論文撰寫和修改工作。預期成果:機械制造技術(shù)設(shè)計是培養(yǎng)機械工程類專業(yè)學生應職應崗能力的重要實踐性教學環(huán)節(jié),它要求學生能全面綜合地運用所學的理論和實踐知識,進行零件機械加工工藝規(guī)程和工藝裝備的設(shè)計。其基本目的是:1) 培養(yǎng)工程意識。2) 訓練基本技能。3) 培養(yǎng)質(zhì)量意識。4) 培養(yǎng)規(guī)范意識。特色或創(chuàng)新之處1、 設(shè)計了一副可以多方面加工的夾具,減少了原材料的應用和所需的工時。2、 設(shè)計了多種加工方案,并對其比較,選出最佳方案。已具備的條件和尚需解決的問題1、一是對鏜床的不熟悉,二是在公差與配合方面的知識所學較少。2、學院圖書館相關(guān)資料有限,并且很多資料不外借處學校,設(shè)計此項目任務重工作量大物力條件有限以及經(jīng)濟上的原因造成難以落實原材料加工出成品3、經(jīng)過努力,設(shè)計達到了預想的成功,由于條件的限制沒能加工出成品,但對于我自己來說已經(jīng)學到了不少東西。指導教師意見 指導教師簽名:2011年 11 月 20 日教研室(學科組、研究所)意見 教研室主任簽名: 年 月 日系意見 主管領(lǐng)導簽名: 年 月 日英文原文Mineral product monorail reduction gear synopsisFirst:what is reducerReducer is a dynamic communication agencies, the use of gear speed converters, motor rotational speed reducer to the Rotary to be few, and have greater torque institutions. The reducer role 1) velocity at the same time increase the output torque, torque output ratio by motor output by slowdown, but the attention should be paid to exceed the rated torque reducer. 2) the speed at the same time reduce the inertia load, the inertia of deceleration than reduced to the square. We can look at the General Motors has a value of inertia. The type of reducer General helical gear reducer has reducer (including parallel shaft helical gear reducer, a worm reducer, bevel gear reducer, etc.), planetary gear reducer, Cycloid reducer, a worm reducer, a planetary friction CVT mechanical machines. Common reducer 1) worm reducer is the main characteristics of a reverse self-locking function, can be larger than a slowdown, input shaft and output shaft axis is not the same, nor in the same plane. But generally larger, transmission efficiency is not high, the accuracy is not high. 2) Harmonic Harmonic Drive reducer is controllable using flexible components to transfer elastic deformation and dynamic movement, not volume, high precision, but the disadvantage is that flexible wheel limited life, impatient shocks, rigidity and pieces of metal relatively poor. Not too high speed input. 3) planetary reducer its comparative advantage is compact structure, the return gap small, high precision, and have a long life span rated output torque can be done great. However, a price slightly expensive, the requirements of parts before assembly 1. Rolling cleaning with gasoline, kerosene other parts cleaning. All parts and Xiangbenna not allowed to have any impurities exist. Gear box and the inner wall (Worm), unprocessed surface has not been coated twice erosion-resistant oil paint, box has the outer surface coated primer and paint color (color requested by host). 2. Parts coated with a face wash after lubricants Second, the requirements of installation and adjustment 1. Rolling installation Rolling bearing inner ring should be installed at the shaft shoulder close to gap must not pass 0.05 mm thick Cypriot feet. 2. Bearing axial clearance of the clearance can not be adjusted bearings (such as deep groove ball bearings), axial clearance of 0.25 to 0.4 mm; the clearance adjustable bearing axial clearance numerical table. Click Tapered Roller Bearings axial clearance; angular contact ball bearing axial clearance 3. Gear (Worm) meshing tooth space available Cypriot side foot of lead or pressure. Will be lead wire on the alveolar, and then turning gear and squash lead wire, measuring two teeth side was crushed lead wire thickness and the size of which is adjacent teeth. 4. Tooth contact dot cylinder gear tooth contact Dot 2-10-4; bevel gear tooth contact Dot 2-11-4; Gearing contact Dot 2-12-4 Third, seal requirements 1. Box partition between the surface does not allow any pads filled, but can be coated or water glass sealant to ensure that the seal; 2. Assembly, the bolt tightening box, before using 0.05 mm Cypriot-foot inspection Covers Block with me and between the sealing surface; 3. Shaft seal should stretch to smear grease. The seal should be installed in strict accordance with the requirements Forth, lubrication requirements 1. Rationally determine the types of lubricants and greases and grades 2. Bearing lubrication fat, grease filled in the general Fatliquor space can be 1 / 2 to 2 / 3. 3. Lubricants should be regularly replaced, the new reducer used for the first time, the operation of oil-7 14 days, according to the situation can be after every 3 to 6 months for first oil. Fifth, the test requirements 1. Empty operation: at rated speed is, anti-running 1 to 2 hours; 2. Load test: at rated speed, rated load operation, the oil temperature balance to date. On the gear reducer, requested the pool temperature is not more than 35 oC, bearing temperature rise no more than 40 oC; the worm reducer, requested the pool temperature not more than 60 oC, bearing temperature of not more than 50 oC; 3. Entire testing process for the smooth operation, noise, not loosening the fixed link, sealed, not with the Sixth, packaging and transportation requirements 1. Protruding shaft and its annex should Oiler packaging; 2. Handling, lifting may not use screw rings and lug all of the above technical requirements are not necessarily listed, and sometimes also by other projects, mainly by the specific design requirements. Seventh. Technical requirements 1. Assembly, all parts cleaning with kerosene, gasoline Rolling cleansing, while the existence of any debris. Oil is not painted wall corrosion coatings twice; 2. Backlash with lead wire mesh test of not less than 0.16 mm, lead wire Backlash may not exceed the smallest of the four times; 3. Used Tu-color dot test. Tooth high point of contact by not less than 40% of contact spots on teeth not less than 50 per cent. Can be used when necessary, grinding or scraping after grinding to improve contacts; 4. Bearing axial clearance should be adjusted: 40 0.05 - 0.1 mm, 55 0.08 - 0.15 mm; 5. Test reducer subdivision surface, the contact surface and seal, oil spills are not allowed. Split-Tu allowed to paint or water glass seal and allow the use of any filler; 6. Engine lubricants to the contents N100 provisions height;Below I introduce our country reduction gear the development present situation First, the domestic reduction gear many by the gear drive, the worm drive primarily, but has the power and the load ratio generally is small, or velocity ratio great and mechanical efficiency excessively low question.Moreover, in the material quality and the technological level also has many weakness, the large-scale reduction gear question is specially more prominent, the service life is not long.The domestic use large-scale reduction gear (above 500kw), many from overseas (for example Denmark, Germany and so on) imports The 60s start few tooth reduction gears and so on difference transmission, cycloid pin gear transmission, overtone transmission which produces has the velocity ratio to be big, volume small, mechanical efficiency higher merit? .But its transmission theory limit, cannot transmit the oversized power, the power all must be smaller than generally 40kw. Because in the transmission theoretically, the technological level and the material quality aspect has not broken through, therefore, has not been able fundamentally to solve the transmission power in a big way, the velocity ratio big, the volume small, the weight light, mechanical efficiency higher these requests basically.The 90s initial period, the home appears three links (gear) the reduction gear, is one kind of outside stable motion gear drive reduction gear, it may realize the great velocity ratio, transmission load ability is also big. Its volume and the weight are all lighter than the dead axle speed reducer gear, the structure is simple, the efficiency is also high.Because this reduction gear three axle parallel structure, therefore caused the power/volume (or weight) the ratio is still small.Also its input axis and the output shaft on the identical spool thread, this do not have in the use many inconveniently. Not only Beijing Institute of Technology develops in successful stable motion speed reducer gear to have outside three link reduction gear merit, but also has the big power/weight (or volume) the ratio, as well as the input axis and the output shaft on identical spool thread merit, is at the domestic leading position.The home has the minority college and the factory and mining enterprise does the research work to in stable motion gear drive certain principles, has published some research paper, in has done some work using the cycloidal tooth crop rotation stable motion reduction gear.Second, the stable motion speed reducer gear principle of work synopsis, the stable motion speed reducer gear is refers to in a counter gear transmission, a gear in the stable motion generator actuation mean plane parallel motion, meshing through tooth profile between, actuates another tooth crop rotation dead axle to decelerate the rotation, the realization reduction gear function.The stable motion generator may use the parallelogram organization, either sine organization or cross slide organization.This achievement uses the parallelogram organization to take the stable motion generator. The stable motion generator may be the hypothesized use parallelogram organization, also may be the entity use parallelogram organization.Has the practical value stable motion gear mechanism for in counter gear organization, therefore may divide into the internal tooth crop rotation stable motion movement and the external tooth crop rotation stable motion movement two kind of situations.Outside the stable motion gear reduction organization, its internal tooth crop rotation stable motion movement, actuates the external gear and makes the deceleration rotation output.This organization also calls three links (gear) the reduction gear. As a result of the internal tooth crop rotation stable motion, two crank centers establish outside the annular gear tooth ring, therefore its size is not compact, cannot solve the volume major problem.? In stable motion gear reduction, its external tooth crop rotation stable motion movement, actuation internal tooth crop rotation deceleration rotation output.As a result of the external tooth crop rotation stable motion, two crank centers can establish in the external gear tooth ring, reduced the organization overall size greatly. Because in stable motion gear mechanism transmission efficiency high, volume small, input output coaxial line, therefore by widespread application prospect.Third, this project technical characteristic and key technologies? 1. this project technical characteristics, in this new stable motion speed reducer gear and domestic and foreign had the speed reducer gear compares, has the following characteristic: (1) velocity ratio scope is big, gets up from I=10, may reach most greatly several thousand.If manufactures the great velocity ratio the reduction gear, then demonstrates this reduction gear the merit.(2) transmission power scope is big: And may connect a body manufacture with the electric motor. (3) structure simple, the volume small, the weight is light.Reduces about 1/3 compared to the existing speed reducer gear.(4) mechanical efficiency is high.95 (5) this reduction gear input axis and the output shaft are on the identical spool thread.This reduction gear see Table 1 with other reduction gear performance comparison. Because lacks the data, various reduction gears power/load ratio which in the table arranges in order is most superior.? Table 1? Each kind of reduction gear comparison model power (kw) reduction gear ratio quality (kg) QI-450? 93 31.5 1820 ZSY-250? 95 31.5 540 NGW-92 88.1 31.5 577 SEW (Germany)? 90 28.61 1300 NP-100? 100 30 400 Note: NP-100 is in the stable motion speed reducer gear, the SEW reduction gear quality contains the electrical machinery.2. this project key technologies? May know by Figure 2, in “stable motion speed reducer gear is by annular gear Z2, external gear Z1 and the parallelogram organization combination becomes.Its transmission principle is: The electrical machinery input rotary motion, the external tooth crop rotation parallel migration, its center of circle path is a circle, makes the dead axle rotation with it meshing annular gear. Because external tooth crop rotation parallel migration, therefore name stable motion gear mechanism.The gear parallel migration needs to have the auxiliary body help realization, may use (612) to sell the axis, the roller takes the hypothesized auxiliary stable motion organization, also may use the eccentric shaft to take the entity auxiliary stable motion organization.In the stable motion speed reducer gear key technologies and the essential craft are the composition parallelogram component size computation and the request processing precision, the gear teeth main parameter choice. These factors will all affect the transmission ability and the transmission quality.Overall speaking, the group cost reduction gear various spare parts all request to have the high precision, they will be deciding the reduction gear overall transmis3. this project survey this project has obtained the Chinese practical new patent, the patent number: ZL95227767.0? .? This project trial produced the first prototype from 1995 (power 2.5kW, after velocity ratio I=32), with some factory and mine cooperation, has one after another designed following several kind of different powers, the different velocity ratio reduction gear.(1) electrically operated on rollers gate uses the reduction gear, power 550W, velocity ratio I=26, is united as one body with the electrical machinery.sion quality. (2) mixer uses the reduction gear, power 370W, velocity ratio I=17.(3) some military goods use two kind of reduction gears, one kind of power 370W, velocity ratio I=23.5; Another kind of power 370W, velocity ratio I=103 two level of transmission reduction gear.(4) steel mill large package rotary abutment reduction gear, power 7.5kw, velocity ratio I=64.(5) steel mill table reduction gear, power 7.5kw, transmission I=11. In this patent foundation, has developed one kind of new ultra-large reduction gear, the power may reach 1000kw, at present is developing subminiature (outlook size for a millimeter level) miniature reduction gear. Graduation design task First, a design Monorail Driver Design reducer Second, the design of the original data 1 Monorail drive reducer Power Rating: 7.5 KW; 2 Monorail reducer drive the total transmission ratio: 15 around; 3 Monorail reducer drive car driven by the side of the output shaft from the race distance of not more than 200 mm; 4 Monorail reducer drive the total length of less than 420 mm, the width is not more than 450 mm and the total height of not more than 690 mm; Third, the equipment and the working environment This can be used to mine underground, open-air, dust, humidity, air quality, bad comparison bad work environment, and the operational requirements of a safe space. Fourth, the design requirements To meet the application requirements under the premise that the minimum cost of manufacturing. From the following aspects considered; (L) to streamline the shape of each parts, machinery simple structure; (2) merge the functions of spare parts, reducing the types or quantities of spare parts; (3) Application of the new structure, new technology, new materials, product reliability; (4) decomposition components, its assembly, the assembly of the most simple structure; (5) similar to parts of the division; (6) standards for similar products by product serial number sequence analysis; (7) The realization of the common parts of the product and standardization. (8) assembly equipment design a map (0), the Six Parts (3), the design specification of a (not less than 30,000 words), and the design of technical and economic analysis.中文譯文一、 什么是減速器減速器是一種動力傳達機構(gòu),利用齒輪的速度轉(zhuǎn)換器,將馬達的回轉(zhuǎn)數(shù)減速到所要的回轉(zhuǎn)數(shù),并得到較大轉(zhuǎn)矩的機構(gòu)。1、減速器的作用 1)降速同時提高輸出扭矩,扭矩輸出比例按電機輸出乘減速比,但要注意不能超出減速器額定扭矩。 2) 減速同時降低了負載的慣量,慣量的減少為減速比的平方。大家可以看一下一般電機都有一個慣量數(shù)值。2、減速器的種類 一般的減速器有斜齒輪減速器(包括平行軸斜齒輪減速器、蝸輪減速器、錐齒輪減速器等等)、行星齒輪減速器、擺線針輪減速器、蝸輪蝸桿減速器、行星摩擦式機械無級變速機等等。3、常見減速器 1) 蝸輪蝸桿減速器的主要特點是具有反向自鎖功能,可以有較大的減速比,輸入軸和輸出軸不在同一軸線上,也不在同一平面上。但是一般體積較大,傳動效率不高,精度不高。 2) 諧波減速器的諧波傳動是利用柔性元件可控的彈性變形來傳遞運動和動力的,體積不大、精度很高,但缺點是柔輪壽命有限、不耐沖擊,剛性與金屬件相比較差。輸入轉(zhuǎn)速不能太高。 3) 行星減速器其優(yōu)點是結(jié)構(gòu)比較緊湊,回程間隙小、精度較高,使用壽命很長,額定輸出扭矩可以做的很大。但價格略貴一、對裝配前零件的要求 :1.滾動軸承用汽油清洗,其他零件用煤油清洗。所有零件和箱體內(nèi)不許有任何雜質(zhì)存在。箱體內(nèi)壁和齒輪(蝸輪)等未加工表面先后涂兩次不被機油侵蝕的耐油漆,箱體外表面先后涂底漆和顏色油漆(按主機要求配色)。 2.零件配合面洗凈后涂以潤滑油二、安裝和調(diào)整的要求 1.滾動軸承的安裝滾動軸承安裝時軸承內(nèi)圈應緊貼軸肩,要求縫隙不得通過0.05mm 厚的塞尺。 2.軸承軸向游隙對游隙不可調(diào)整的軸承(如深溝球軸承),其軸向游隙為0.250.4mm;對游隙可調(diào)整的軸承軸向游隙數(shù)值見表。點擊查看圓錐滾子軸承軸向游隙;角接觸球軸承軸向游隙 3.齒輪(蝸輪)嚙合的齒側(cè)間隙可用塞尺或壓鉛法。即將鉛絲放在齒槽上,然后轉(zhuǎn)動齒輪而壓扁鉛絲,測量兩齒側(cè)被壓扁鉛絲厚度之和即為齒側(cè)的大小。 4.齒面接觸斑點圓柱齒輪齒面接觸斑點2-10-4;圓錐齒輪齒面接觸斑點2-11-4;蝸桿傳動接觸斑點2-12-4 三、密封要求 1.箱體剖分面之間不允許填任何墊片,但可以涂密封膠或水玻璃以保證密封; 2.裝配時,在擰緊箱體螺栓前,應使用0.05mm的塞尺檢查箱蓋和箱座結(jié)合面之間的密封性; 3.軸伸密封處應涂以潤滑脂。各密封裝置應嚴格按要求安裝四、潤滑要求 1.合理確定潤滑油和潤滑脂類型和牌號 2.軸承脂潤滑時,潤滑脂的填充量一般為可加脂空間的1/22/3。 3.潤滑油應定期更換,新減速器第一次使用時,運轉(zhuǎn)714天后換油,以后可以根據(jù)情況每隔36個月?lián)Q一次油。五、試驗要求 1.空載運轉(zhuǎn):在額定轉(zhuǎn)速下正、反運轉(zhuǎn)12小時; 2.負荷試驗:在額定轉(zhuǎn)速、額定負荷下運轉(zhuǎn),至油溫平衡為止。對齒輪減速器,要求油池溫升不超過35oC,軸承溫升不超過40oC;對蝸桿減速器,要求油池溫升不超過60oC,軸承溫升不超過50oC; 3.全部試驗過程中,要求運轉(zhuǎn)平穩(wěn),噪聲小,聯(lián)接固定處不松動,各密封、結(jié)合處不 六、包裝和運輸要求 1.外伸軸及其附件應涂油包裝; 2.搬運、起吊時不得使用吊環(huán)螺釘及吊耳以上技術(shù)要求不一定全部列出,有時還需另增項目,主要由設(shè)計的具體要求而定。七、技術(shù)要求 1.裝配前,所有零件用煤油清洗,滾動軸承用汽油清洗,不許有任何雜物存在。內(nèi)壁涂上不被機油腐蝕的涂料兩次; 2.嚙合側(cè)隙用鉛絲檢驗不小于0.16mm,鉛絲不得大于最小側(cè)隙的4倍; 3.用涂色法檢驗斑點。按齒高接觸點不小于40%;按齒長接觸斑點不小于50%。必要時可用研磨或刮后研磨以便改善接觸情況; 4.應調(diào)整軸承軸向間隙:40為0.05-0.1mm,55為0.08-0.15mm; 5.檢驗減速器剖分面、各接觸面及密封處,均不許漏油。剖分面允許涂以密封油漆或水玻璃,不允許使用任何填料; 6.機座內(nèi)裝N100潤滑油至規(guī)定高度。八、下面我介紹我國減速器的發(fā)展現(xiàn)狀(一)、國內(nèi)的減速器多以齒輪傳動、蝸桿傳動為主,但普遍存在著功率與重量比小,或者傳動比大而機械效率過低的問題。另外,材料品質(zhì)和工藝水平上還有許多弱點,特別是大型的減速器問題更突出,使用壽命不長。國內(nèi)使用的大型減速器(500kw以上),多從國外(如丹麥、德國等)進口。60年代開始生產(chǎn)的少齒差傳動、擺線針輪傳動、諧波傳動等減速器具有傳動比大,體積小、機械效率高等優(yōu)點?。但受其傳動的理論的限制,不能傳遞過大的功率,功率一般都要小于40kw。由于在傳動的理論上、工藝水平和材料品質(zhì)方面沒有突破,因此,沒能從根本上解決傳遞功率大、傳動比大、體積小、重量輕、機械效率高等這些基本要求
收藏